Fuel injection pump



HIGH SPEED Ap 30, 1957 R. 1.. SHALLENBERG ETAL 2,790,432

FUEL INJECTION PUMP Filed D90. 17. 1954 2 Sheets-Sheet 1 0W SPEED J08 J11 J15 121 Apr 30, 1957 R. L. SHALLENBERG ETAL' 2,790,432

FUEL INJECTION PUMP Filed Dec. 17, 1954 2 Sheets-Sheet 2 25' w 73 7g 1 PF nexed -drawings, Whereinz,

United States Patent 2,790,432 FUEL INJECTION PUMP.

Robert-L. Shallenberg, Westchester,and WaIterA; Parfish,- Jr., Dolton, lll., assignors. tolnternational Harvester. Company, a corporation of New- Jersey; 4

Application December 17, 1954, Serial No. 475,979 '9 Claims. (Cl. 123-139) containing a pumping portion which delivers a measured quantity'of fuel under pressure to the distributor port concurrently with each registration thereof with affuel linegport, and the rotor structure also including a meter.- ing 'and'timing portion in control of the pump portion to determine the quantities of fuel delivered andj-th'e time This invention is an imthat the delivery commences. provement over U. S. Patent 1,772,828 to 'F. Egersdorfer. g An important object of'this invention, is theprovision of a fuel injection pump of the above character wherein thefuel distributing portion of the rotor structure is at one end of the pumping portion anldthe fuelmetering and timing portion is at the other end ofthe pump-ing portion. This arrangement improves the space factor of the parts of the pump inasmuch as the pulsating chamber; of the pump can communicate in opposite axial directions respcctivelywith the distributing portion and-themetering and timing portion, and manual and speed responsive control means for the metering and timing portion of the rotor-structure can be assembled with respect thereto without interference with or from parts of the distributing portion.

A further object is the provision of a rotorstructure wherein the pumping portion contains a transverse bore for radially opposed pistons actuated by an internally Fig-. llisv axsectionalview takenthrough the easing: of a preferred embodimentof the invention, the-view beinglongitudinally of the pump'rotor structure and showing. parts-in section other than the casing, and

portions of sorne;parts being broken away-for clarity;

Fig. 2 is an end vi'ewof the pump looking at the'end disposed to the right in" Fig. 1', there being a portion of the upper part of :the casing broken away to'expos parts'of the control.shaft-and'linkage for the pump; n; Fig.3 zis a:-tr'ansverse-sectional -view taken at the line I 3i.-3 of Fig. 1 through. the metering portion of the rotor structure and through the fuel metering sleeve encircling thistportion of the rotor structure,- the view also; illustrating 'in dot dashlines an arm. extending radially: from.,thesl.eeve and'rigidly assembled therewith for mparting-.manual rotative: adjustment to the sleeve;

' Fig.4 is: a vi'ew taken-similarlyto Fig. 3 through the lobed annular cam surrounding the pump portion of the rotor structure. I r

A further object of this invention is theposition of a pump rotor structure wherein the pump chambercommunicates with the distributor portion and withfthe metering and. timing portion by an axial borewhichshas a radially opening spill port controlled by an internal groove within a sleeve about the rotor strucmretocomtherefrom after a selectable interval. of pumpstroke to timingqports; a-nd timing; sleeve of. the pump, this view being at the position indicated by the line 44 in Fig.1;

. Fig.5 ;is;-airtr. nsverse sectional view taken on the line 5l of Eigjl through the pump-portion of the rotary structureand-;--throl,1gh a fixed annular. cam internally lobed for operating pistons ofthe pump;

'.-;Fig, 6, is at transverse-sectional view taken at the section indicated ,by the :line 66 in Fig. 1' through the distributor: portionv of: the pump.

Referring -,now to Fig.1 the-pump will be seen to com-prisey'a casing enerallyindicated, 10. Thisicasing has a leftend-wa11-.--11 containing an opening 12. A rightend ;w,all'13 of the casing has an opening. 14 c0- axial with the opening 12. Four recess-headed cap screws 15 shown in Figs. 1 and 2 extend through and are employed, for mounting a distributor head 16 anda gear; hump casing -17 onto the exterior side of the end wall-13. A tubularextension 18 of thedistributorhead 16 extends into the opening 14 of the end wall 13 wherein such extension is piloted.

A rotor :structureal9 has 'an enlarged pumping portion 20, a metering andtirning portion 21 at the left end of the pumping portion 20, and a distributing portion 22 at theoppositeor right end of the pumping portion.*

relation-exists between the cylindrical outer periphery of the distributor-portion 22 of the rotor structure and terminate fuel delivery and thus etiect'metering under high pressure, and the axial bore within'the rotorist'ructure also having a timing port controlled by asimilar sleeve of which the internal groove is adjustable with this sleeve,. toterminate registration. of the timing port'therewith at selectable times to determine;when bypassof fluidstherethrough from the pump shall cease and .-pumping stroke of the pump become effective for developing injection pressure within the fuel. p A further object is the provision of metering and timing sleeves of the aforesaid character wherein ,the internal grooves are directed helically about the axis of the rotor to adapt the sleeves to respectively change the quantity of fuel pumped and the timing of the Pumping responsively to change in the axial positions of these sleeves as well as the rotative position ofthe metering- Slfiv;

The above and other desirable objects inherent-in and encompassed by the inventionare 'eluciated in the-ensuing specification, the appended'claims and th'e 'an- .the cylindrical inner peripheryof-the distributor head; 16

and extension 18 The rotor structure 19 is continuously driven by a drive shaft or coupling member 24' keyed .at 25 to the left end of suchstructure.

Thepumpingportion of the rotor structure as illus-. trated. in Figs. 1 and Sincludes adiametric bore. 26 in Y which radially opposed pistons 27 are reciprocated in timed relation so as to be simultaneously moved toward one another .into their, most radially inward positions illustrated in Figs. 1 and 5. alternately with being simultaneously moved apart radially outwardly, so as to alternately contract andexpand a. pumping chamber 28 formed withinthe bore "26 between the 'oppo sed inner ends of these pistons.- Each piston ha's'an outer-tappet 29'Wherein there is journalled a roller 30 adapted to rotate about the-inner periphery of an annular cam member 31 mounted'non-rotatively within the casing 10. There are four internal lobe's 32 within'the cam for causing the pistons 27 to perform four cycles of expansion and contraction of the pumping chamber 28 during eachlrevolutionof. the rotor structure 19."

.Fuel is deliveredto. the'purnp through an inlet' (not showulxto the fuel feed pump; 33 including the above mentioned casing 17 and pumping gears 34 of which one is shown in section in Fig. 1. This gear 34 shown in Fig. l is driven continuously with the main pump rotor structure 19 through a non-circular axial projection 3501 a screw plug 36 threaded at 37 into a threaded recess 38 in the right end of such rotor structure, thence through a tubular coupling member. 39. and a hub member/l for the gear 34. This feed pump including the gear -34 is adapted to deliver liquid fuel at a constant nominal pressure, 50 pounds per square inch, for example, into an inlet passage 41 which'leads from the pump casing -17 through the distributor'headlG into. an annular channel 42'formed in thei'outer face of the end wall 13 .of'the main casing 10. Thelinlet passage 41 is also shown in Fig. 6 as is the annular channel'42 and four radial passages 42a which lead inwardly from the channelv42 through the tubular hub of the distributor. These radial'passage portions 42a are spaced apart 90 about the axis of the rotor structure and are successively communicated with by an outer end portion or port 43a of 'a' radial inlet passage 43 in the rotor structure. 'Radialinlet passage 43 communicates with the pump chamber 28 through a portion of an axial rotor passage 44. The circumferential orientation of the radial inlet passages 42a with respect to the cam. lobes 32' of the main pumpis such that the inlet port 43a registers with a succeeding one of such passages 42a each time the pump chamber 28 is expanded pursuant to the tappet rollers descending a trailing profile portion 32a of the cam lobes 32; see Fig. 5. The roller tappets 30 force the pistons 27 together for contracting the pump chamber 28 each time these rollers ascend the approach profiles'32b of a pair of diametrically opposed cam lobes 32.

Normally during operation of the device, that is, when 7 the device is set for delivering fuel, contraction of the pump chamber 28 forces fuel rightward through the passage 44 past a delivery check valve 45 into the chamber 46 of such valve which includes an annular groove-like space 47 between the inner end of the screw plug 36 and an opposed end of an annular ring 48 screwed into the threaded portion 37 against a valve seat member :49. An outlet port 50 of the distributor portion 22 communicateswith radial outlets 52 of which there are four in number spaced equidistantly and radiating through the distributorhead 16. These radial passages 52 communicate-attheii' outer ends'with couplings 53 of which each has'a recess 54 for receiving the end'of a respective fuel line'leading to an engine uponwhich the device is "adapted to be mounted. Couplings 53 all appear in Fig. '2. The radial passages 52 of the distributor head 1621s shown in Fig. '6 are so oriented circumferentially at the rotor-axis with respect to the internal camlobes 32 of the annular cam 31 that the distributor outlet port' 50 -registers with a respective one of such passages52 dur ing each contraction of the pumping chamber 28. v V

The metering and timing portion 21 of the rotor structhre carries a timing sleeve 55 cooperative with ports 56 of the axial passage 44 to determine the time during the contraction period of the pump chamber 28 that fuel delivery commences past the delivery check valve 45 of the combustion chambers of the engine. A metering lsleeve 57 controls the time; that fuel can spill outwardly through a metering or spill port 58 to terminate delivery -.from thecontracting pumpingchamberlS past the delivery valve 45 and thereby determine the quantity of -fuel pumped attendant to each injection impulse. Timing-sleeve 55 can move only axially of the rotor struc- 'ture because of being constrained against rotation by a -casing=mounted pin 59 which projects intoan axial groove -60-in the outer periphery of such sleeve; see Fig. '4. Metering sleeve 57 is adapted to rotate aswell as move axially on the rotor metering portion '21. A coupling :band 61 'for connecting the control sleevesSS and57 for aaxialmovement in unison while permitting relative-rota 4 V tion by sleeve 57 is press fitted on a shoulder 62 of sleeve 57 and has an in-turned flange 63 hooking over flange 64 of the sleeve 55.

Each of the control sleeves 55 and 57 has a sliding sealing fit at its inner periphery with the cylindrical outer periphery of the coritrol or metering and timing portion 21 of'the rotor'structure excepting for that portion of the periphery of "the control portion 21 which registers with internal grooves within the sleeves 55 and 57. "Timing sleeve 55 'has fourgenerally axial helical grooves 65- within its inner periphery. Each of these grooves communicates with the right end of the sleeve 55 as viewed in Fig. l so that when any of the. grooves is in registry with the'tirn'ingport's 56 fuel'canfescape through these ports and the registered groove 65 to prevent the development of enough fuel'pressure-in the pump chamber 28 for forcing 'fuel'past the delivery check valve 45. These internal grooves 65 are 'so' oriented.circumferentially of the rotor axis with respect to the camlobes 32 of the piston pump that the timing ports 56 are in registration with a pair of the diametrically opposite grooves 65 when the pump chamber 28 begins contraction. Consequently injection cannot commence until the rotor has rotated far enough to carry the timing ports 56 out of registration with these'tirning grooves. Thus timing or the beginning of injection can be varied by moving the timing sleeve 55 axially. With the spiral grooves 65 having the direction of pitch illustrated in Fig. 4, axial movement of the timing sleeve 55 to the right as viewed in Fig. 1, while the rotor structure rotates in the direction indicated by the arrow inFig. 4, will cause the timing ports 56 to vdepart from partial registration with the grooves 55 nearer the begin ing of the compression or contraction phase of the pump chamber 28 and thus advance the timing. Axial adjustment of the timing sleeve 55 is under control ot a governor device which will be explained later. 7 It will be noted there are four exterior axial grooves-60, a, 60b, and 600 in the timing sleeve 55. Each of these grooves is adapted to cooperate with the constraining pin .59 and they are selectively placeable in cooperative relation with the pin 59 attendant to retraction of such pin 'endwise and advancement thereof into any one of these grooveswhich is placed in registration thereof attendant to rotation of the sleeve 55 upon the rotorportion 21. The grooves 60, 60a, 60b and 600 are progressively spaced circumferentially of the sleeve 55 in a graduation of difqferentamounts with respect tothe location of the grooves circumferentially of such sleeve. Therefore by placing .difier'ent ofthese exterior grooves in cooperative relation withfthe pin 55 the timing range of the internal timing grooves 65 can be adjusted as desired. 4

' Theinternal spiral grooves 66 of the metering sleeve .57 are so disposed circumferentially of the :rotor structureiaxis, while thissleeve is set to cause fuel delivery by thepiston pump, that such grooves are out of registration with the metering or spill ports 58at the time the pumping chamber 28 commences'its compression or contraction. At a later time during continuation of the contraction of the pumping chamber the ports 58 arrive in registry with a pair of diametrically opposite internal-grooves 66 to allow the fuel to spill from the contracting pumping chamber outwardly through the ports 58 and the grooves 66 to the left end of the vmetering sleeve 57 as viewed in Fig. I. This excess fuel simply spills into the pump casing 10. Thus the casing 10 acts as a sump for spilled fuel, and a jconduitgnot shown, leads from the casing'lfl through a' of fuel to be pumped for injection through the delivery passages 52 of the distributor 16. Thus*by changing-the rotative position of the metering sleeve 57 the quantityof fuel delivered by the piston pump for vdelivery to the 'combustion chambers can be selectively varied.

Also it will be noted in Fig. 3-that the spiral pitchof the metering grooves 66 is such vthat axial movement of this'sleeve to the right as viewed in Fig. 'l'Will enable the spill ports 58 to arrive in registry withthe "grooves sooner and thereby correspondingly diminish the amount of fuel pumped per stroke of the pistons 27.

Manual rotative settingof the metering sleeve 57 is obtained by the use of a manually s'ettablejlever:67, .Fig. 2, which is mounted non-rotatively upon a cross shaft 68. End portions of the shaft 68 are mounted within bearings 69 and 70 in'opposite walls 71 and 72 of a control compartment on the upper side of the casing 10. A cover cap 74 of the compartment 173 is r'emovably held in place by long cap screws 75. A sleeve 76 is held. non-rotatively upon the cross shaft 68 by a pin 7.7." An arm 78 fixed upon the sleeve 76 has a cross pin 79 in its end portion remote from the sleeve 76, and this cross pin 79 has a spherical end portion 80 universally pivoted. within a spherical socket 81 within a head 82 constituting the upper end portion of a turn-buckle -t'ypelihk 83. Link 83 is indicated in phantom in Fig. 1 by dot dash lines. A similarly socketed lower end member 84 of the link 83 universally pivotally receives a spherical end portion85 of an operating stem 86 anchored in and projecting'radially outwardly from the metering sleeve 57. Rocking of the cross shaft 68 by the manually operated lever 67, Fig, 2 causes swinging of the arm 78, Fig. 1, to raise or, lower the link 83. which is operable through the, stem 86, Fig.3, for selectively changing the rotative position of the meter.- ing sleeve 57 and thus changing the amount, of fuel delivered by the piston pump to the engine. combustion chambers. v i

A second arm .88, projecting upwardly from the sleeve 76 and constrained against rotation relatively thereto has a center line projecting upwardly to a positionfdesignated Low Speed which indicates that the manual control lever 67 is at this time in a position causing'the' metering sleeve 57 to be in a'rotative positionc-ausing.the engine to operate at Low Speed. Manual..lever 67 can. be operated for rotating the shaft 67, the sleeve 76 and the arm 88 to the position designated Fuel Shut-off. At tendant to this setting the metering sleeve 57 will be rotated sufiiciently far clockwise as viewed in-Fig. 3 to-cause the spill ports 58 to register with diametrically opposite .of the grooves 66, at all axial positions of the sleeve-57, before timing ports 56 have moved out of registry with the ti n ing grooves 65 within the timing sleeve Consequently when the control is adjusted into the Fuel Shut-off. position the pistonpump is effective for pumping-fuel'outwardly only through the spill ports 56 and 58 so that no fuel can be delivered past the delivery check valve 45.

By adjusting the manual control lever 67 until the'lever 88 is moved into the High Speed position,-the-metering sleeve 57 will be rotated sufliciently 'far counterclockwise, Fig. 3, that any axialpositionof the sleeve attainedresponsive to engine'speeds not exceeding rated speed, sufiicient fuel will be delivered by the piston'pump for operating the engine at substantially rated load.-

The speed and torque load upon an engineto which fuel is delivered by the present device iscontrolled by that portion of the device now to be described. A left end portion of the rotor structure 19 has an inertia weight carrier 90 mounted thereon and constrained for=rotation therewith by a pin 91. Pivot pins 92 on the carrier 90 pivotally carry centrifugal weights W having respective toe portions 93 which bear against the left end of a sleeve 94, Fig. 1, to shift this sleeve rightward; upon the rotor structure 19 attendantto the shaftv rotating ,fast enough to cause the weights W to swing radially outwardly from the shaft or rotor structure. Axial force is transmittedfrom the sleeve 94 to the metering sleeve 57 through a ballbearingfunit 95. 'A pair of rollers 96, one b'e'irig shown in dotted lines in'Figfl, are respectively upon thje furjcations of a forkedl'ever 97, andthese rollers96 bear against a r'adialfi'ahge ofthe metering sleeve57, which flange also forms a race of the ball heating unit 95. upper .end of the lever projects through anopeni'ng 919 of a cup-like member 1100 depending downwardly through an openirig'lfll in the upper wall 102' of. the casing 10 This"cuplikewall'member100 journals a shaft 103'up'on which a hub 104 ofthe lever 97 is mounted and constrained against relative rotation by a pin. 105 Also constrained for rotation with the hub 104 of the lever 97i's a torque spring h'older ir'1e'rnber106 having "end, portions 107, 108be'tweeri which a leaf spring 109 is suspended. An adjustable stop memben l09iz upon the spring holder 106' limits the distancethe torque spring v1 09 "1"1iay he bowed in the direction of bowing illustrated in Fig'.'fl.

A lever 110 shown partially behind the torque spring holder 106 in Fig; 1, is pivotally mounted at, its lowe'rend upon the shaft 1.03:. The upper end of this lever carries a pinl-l lthroughwhich[this-lever is adapted to exert compressive force against. a helical governor spring 112 havingitsleftend pivotally connectedwith, a casing- -mounted -h racket' 11 3 by a pivot connection 114. A second. pivot pin, -115, in the upper end of the lever 110 pivotally mounts the left end of a rod 116 which projects slidably through a'bore 117 of a cross pin 118 pivotally mountedin the lever 88- A threaded portion 119 of the rod 116 h'as'j an internally threaded stop member, 120 mounted thereon for abutment, against the cross pin 118 during certain conditions of operation, and'the axial position ofth'e stop memberlltl upon the rod116 i's'maintained by ailock nut 1212" v coum rqlnckwis'e pivoting 0f the torque spring carrier 106 with the forked-lever 97 arid the shaft. 103 carries a mid-portion of the torque; spring 109 against a head 110ajof a threadedfstem ,110b rotatively and axially adjustablewithin an internallyv threaded member 110:: com? prising an element ofjthe leve'r' 110.. thus establishing a yieldable connection between the pivoted leaf springcarthe adjustment of the threadedstem 1105;

rier 106 'and thel'e'ver 110. A lock nut lltldmaintains;

Ope'i'tttiolt ofthe apparatus Rotorstructure19 is connected with the-engine ,to which fuel isqto be supplied 'by the app ratus by means of the drive. shaftor couplingg24 so. that the rotor structure will--rotate .at one-half crank-shaft speed ofa .four cycle four. cylinder internal combustion engine. A pump designed'for an enginewith va different number of cylinders would 1 have :a: correspondingly different number of cam lobes 32and fuel line deli-very passages 52-. Fuel is delivered'underpressure to the combustion chambers .of the four cylinder-engine; respectively through conduits (not shown) connected with the fuel outlet couplings 53,. Figs. land-2.

It will first be assumed the manual control for vthe pump has :been set ;so the lever 88 occupies the Low Speed position shown in Fig. land that the engine has just been .started. The rotor- 19 will be rotated in the direction indicated :by thearrows associated therewith'in Figs. '1, 3, 4, 5 'and'6.- Inthis manual setting the mtering' sleeve 57 .willbe advanced onlytslightly counterclockwise, Fig. 3, from: the Fuel :Shut-oif position therefor, When-the engine first starts the rotor structure '19 will be rotating at a';.very slow speed. so the governor weights W will-be in their radially inner positions illus-J trated in Fig; Consequently,'the1 control sleevesand 57 will be near theirleftmost settable positions illustrated in Fig. 1 so the metering spill ports 58. will-register .which the manual control has been set.

'the desired speed of the engine. frotation of the control shaft 68 is operable through the and the rotor structure 19 to accelerate rapidly until .attaining a speed corresponding to the Low Speed.at At this time the metering sleeve 57 will have been moved far enough rightward by the governor weights W that the helical grooves 66 of this metering sleeve will be reached in registration by the metering ports 58 to diminish the amount of fuel delivered to the engine and prevent further acceleration thereof above the selected Low Speed.

Higher speed for the engine is attainable by manual adjustment of the control lever 67, Fig. 2, to rotate the control shaft 68, Fig. 1, further counterclockwise toward the High Speed position a distance depending upon Such counterclockwise arm 78, the vertical control link 83, and the arm 86, Fig. 3, to effect counterclockwise rotation of the metering sleeve 57 as viewed in Fig. 3. V This causes the metering ports 58 to. arrive in'registry with the spill grooves 66 fat still a later time in each contraction phase of the piston pump, wherefore argreater quantity of fuel is delivered to the engine. When the engine attains the speed corresponding to the selected higher speed setting of the manual control, the corresponding faster rotating rotor structure 19 will have caused the governor weightsW to have moved out far enough to shift the metering sleeve 57 far enough rightward, Fig. 1, that the internal spill grooves 66 of this metering sleeve will be registered with earlier by the metering ports 58 to prevent the delivery of fuel in an amount that would cause the engine to accelerate beyond this selected speed. 7

' When it is desired to stop the engine the manual control lever 67, Fig. 2, will be operated for rotating the control shaft 68, Fig. 1, into the position causing the arm 88 to occupy the Fuel Shut-off position. This clockwise rocking of the arm 88 in Fig. 1 will lift the control link 83 for rotating the metering sleeve 57 sufliciently far "clockwise, Fig. 3, that the metering ports 58 will register 'with the spill grooves 66 prior to the timing ports 56, Fig. 4, moving out of registration with thetiming spill grooves 65 of the timing sleeve 55. Since all of the fuel pumped by the piston pump will then be able to spill outwardly through the timing ports 56 and metering ports 58, no fuel will-be delivered to the engine which will cometo rest.

Considering again the condition of operation when the manual control lever 67 has been operated for rock'- -ing the control shaft 68, Fig. 1, into a high'speed position, the ensuing acceleration of the engine and of the rotor shaft 19 in attaining the selected high speed causes the governor weights W to move radially outwardly to assume a position correlated with this 'selected speed. As the weights W move outwardly andshift the sleeve 94 and the control sleeves 57 and 55 rightward,s'i mu1taneously the lever 97 is caused to pivot counterclockwise as viewed in Fig. 1. Counterclockwise movement of the lever 97 also causes counterclockwise movement of the shaft 103 and of the torque spring holder member 106 about the axis of the shaft 103. This presses thetorque spring 109 against the head 110a of the stern 110b anourited on the lever 110, and thus tends 'to pivot the lever 110 counterclockwise about the axis ofthe shaft 103 against the force of the governor spring 112. The force exerted by the spring 112 exceeds that necessary to how the leaf spring 109 wherefore before counterclockwise pivoting of the lever 110' occurs the clockwise moviug holder member 106 will :first fully compress the leaf spring 109against the stem head 110a to carry themid portion of this leaf spring against the headed jl eft erid of thest'op member 109 After thusenergizing itheleaf torqu'e'spring 109, further radial outward movement of thegovernor weightsW and counterclockwise pivoting of-the lever 97 and of the torque spring holder 106 will exerta force directly through the spring 109 against the head 110:: to cause the lever'lltl to pivot in' unison with the lever 97 attendant to compressing the governor spring 112. This-counterclockwise pivoting of the lever 110 causes the rod 116 to slide axially within the bearing 117 of the pin 118 in the lever 88 to retract the stop member 120 from such pin 118. This movement of the various parts movable with the forked lever 97 ceases when the governor spring 112 is compressed far enough to exert suflicient counterforce to-balance the inertia force developed by the governor weights W attendant to attainment of the selected higher speed of the engine.

Now as load is applied to the engine it will tend to decelerate wherefore the force of the compressed governor spring 112 will prevail over the slightly diminished force exerted by the inertia weights W so that the levers 110 and 97 will be rocked clockwise about the shaft 103 to move the metering sleeve 57 leftward for increasing the amount of fuel fed to the engine and limiting the deceleration thereof. A further increase in load upon the engine will further diminish its speed and that of the governor to enable the spring 112 to further expand and move the metering sleeve 57 further leftward to additionally increase the fuel delivered to the engine and stabilize the same at a lower speed. When the engine attains a condition of being subjected to a load equal to its rated load the stop member 120 will abut against the cross shaft 118 in the arm 88 to prevent further expansion of the governor spring 112 so that any additional fuel fed to the engine in response to further deceleration thereof under overload conditions will be under control of the torque spring 109 which, it will be recalled, is in an energized compressed condition against head 110a tends to pivot the spring holder 106 and the forked lever 97 clockwise about the shaft 103 and can effect a limited amount of such pivoting to move the metering sleeve 57 further leftward in response to deceleration of the engine attendant to assuming a maximum load condition requiring engine lugging.

At slower engine speeds the timing sleeve 55 will be held in a more leftward position by the governor than at higher engine speeds. By examining Fig. 4 it will be seen that the timing spill grooves are spiraled in the direction that when the timing sleeve is in the more leftward position of Fig. l the timing ports 56 will move out of registry therewith later and, therefore, cause the injection pressures to commence at a later time than when the sleeve is in a more rightward position corresponding to higher engine speed. Therefore, this sleeve is moved in accordance with governor speed to advance the timing or commencement of injection when the engine is running at higher speed. The desirability of such timing control is well recognized. by those skilled in the art. Having described a single preferred embodiment of the invention with the view of clearly and concisely illustrating the same we claim:

1. In a fuel metering pump; a rotor structure including a pump portion, a metering portion and a distributor portion, said pump portion having a pumping chamber and including means for alternately expanding and contracting such chamber a plurality of times attendant to each revolution of the rotor structure; port means for adr'nitting fuel to the chamber during expansion thereof; means providing a plurality of fuel delivery passages associated with the distributor portion; the distributor portion having a port communicative with the pumping chamber, said port successively communicating withthe delivery passages during rotation" of the rotor and during-respective} contractions 'of the chamber; metering means comprising aspill' port and a timing port in the metering portionof the rotorstrpcture and communicatmeans for admitting fuel to the chamber, spill port masking means associated With. the metering portion and having spill channel means extending helicallyv of the metering portionforregistration with thespilltport to facilitate the spilling of fuelfrom the'pump :chamber through suchport during suchlregistration, timing port masking means associated with thetiming portforvperiodically masking such ,portduringrotation of the rotor structure subsequent to each masking of the spillport by the spill port masking means and thereby initiate the creation ofinjectionpressure f thefuel in the pumping chamber, the spill channel.;means being oriented circumferentially. of the rotorzstructureazto incur'registration of the spill port therewith subsequent to commencement of eachacontraction of the pumping ch'amberymeans for adjusting the spill port'masking means axially of the'rotor structure to change .the time after commencement of pumping.chamber'contraction that registration of the spill port with the spill:channel means occurs; and. means operable for adjusting thespill port masking means rotatively of the rotor structure independently of adjustment of the timingport masking means for also changing the time after commencement of chamber contraction thatrregistration of the spill;port with the spill channel means occurs.

2. In a fuel metering pump; a rotor-structure including a pump portion having a pumping chamber; means for alternately expanding and contracting said chamber a plurality of times attendant to each revolution of said structure; port means for admitting fuel to the chamber during each. expansion thereof; the rotor structure having a distributor port communicative with the pumping chamber and revolvable attendant to rotation of said structure; means providinga plurality of fuel delivery passages successively communicative with the distributor port during, rotation of the rotor and during respective contractionsof the chamber; metering means comprising a spill port and a timing port in'therotor structure and revolved thereby attendant to rotor structure rotation, such spill port communicating with the pump chamber independently of the port means for admitting fuel to such chamber, a spill port masking sleeve journalled on the rotor structure and having internal spill channel means extend ing helically of the rotor structure axis for registration with the spill. port to facilitate the spilling of fuel from the pump chamber through such port during such registration, timing port masking means associated with the timing port for periodically masking such port during rotation of the rotor structure subsequent to each masking of the spill port by the spill port masking sleeve and thereby initiate the creation of injection pressure of the fuel in the pumping chamber, the spill channel means being oriented circumferentially of the rotor structureto incur registration of the spill port therewithsubsequent to commencement of each contraction of the pumping chamber, means for rotatively adjustingthe spill port masking sleeve upon the rotor structure independently of adjustment of the timing port masking means to change the time after commencement of pump chamber contraction that registration of the spill port with the spill channel means occurs, and means for adjusting the masking sleeve axially of the rotor structure for also changing the time after commencement of chamber contraction that registration of the spill port with the spill channel means occurs. I a

3. In a fuel metering pump; a rotor structure including a pump portion having a pumping chamber; means for alternately expanding and contracting said chamber a plurality of times attendant to each revolution of said structure; means for admitting fuel to the chamber during each expansion thereof; the rotor structure having a distributor port communicative with the pumping chamber and revolvable attendant to rotation of said structure;

means providing a plurality of fuel delivery passages successively communicative with the distributor port durpumping chamberandrevolved attendant to rotorstructurerotation; masking. means =.for said timing port and having timing channel means'extending axially of the rotor structure andzwithwhich the timing port registe'rs at the beginning :of each pumping chamber contraction to facilitate spilling of fuel from such lchamben-the' rotor structure revolving the timing port out of registration with the timing channelr'mearisrduring pumping chamber contraction to incur masking of the timing. port 'by the timing port maskingmeans and thusiinitiate fuel delivery through the distributor port, the" timing port masking means being adjustable axially :of therotor'structure, means for'movingithe'timing port masking means axially of the rotor structure, and means for controlling the position of such timingport masking means :rotatively of the rotor structure .attendantfto such axial moving thereof to vary, the 'time'the timing port revolves out of registration with the timing channelameans and thus'vary the time of initiating fuel'delivery.

4. In a fuel metering-pump; a rotor'structure including a pump portion having a pumping chamber; means for alternately expanding and'contracting' said chamber a pluralityof times :attendant to each'revolution of said structure; meansfor'admitting fuel to the chamber during each expansion thereof; the rotor structure having a distributor, port communicative with the pumping chamber and revolvable attendant IO rotation of said structure; means providinga plurality of fuel delivery passages successively communicative with the distributor port during rotation of the rotor and during respective "contractions of theiehamber;-'the rotorstructurealso having 'a spillport and atiming port spaced apart'axially thereof and :opening radially/outwardly of such structure, said ports being communicative with the pumpin'g' chamberg-a spill port metering sleeve ijournalled on the rotor structure for masking the spill port but having-internal spill Chan: nel means extending helically of the rotor'structure axis for registration. with the spill port to facilitate spilling of fuel from the pumpvchamber, the spill channel means being oriented circumferentially of the'rotor structure to incur registration of thespill'port therewith subsequent to commencement of each contraction of the pumping chamber, said sleeve being adjustableaxially relatively to the rotor structure to change the time aftercoinrnencement of the pumping chamber contraction that registration of the spill port with the s'pill channelmeans occurs and also being rotatively adjustable to change the time that such registration ofthe'spill port with the spill channel means occurs; a timing sleeve .mounted for axial adjustment on the rotor structure for masking the timing sport but having internal timing channel means extending timing sleeve axially of the rotor structure being-operative to change the time that the timing port arrives in masking relation with the timing sleeve, means for constraining said sleeves for axial movement in unison'while facilitat ment thereof, manually settable means for selectively changing the rotative position of the metering sleeve, and means responsive to the rotational speed of the rotor structure for changing the axial position of said sleeves.

5. In a fuel metering pump; a rotor structure including a pump portion having a pumping chamber; means for alternately expanding and contracting said chamber a plurality of times attendant to each revolution of said structure; means for admitting fuel to the chamber during each expansion thereof; the rotor structure having a-distributor port communicative with the pumping chamber and revolvable attendant to rotation of said structure; means providing a plurality of fuel delivery passages successively communicative with the distributor port during rotation of the rotor and during respective contractions of the chamber; metering means comprising a spill port in the rotor structure and revolved thereby attendant to rotor structure rotation, and port masking means adapted to uncover the port at selective intervals subsequent to each contraction of the pumping chamber; and timing means comprising timing port means which opens radially outwardly of the rotor structure and communicates with the pumping chamber, a timing port masking sleeve slidably mounted on the rotor structure and having internal timing groove means extending axially thereof and with which the timing port means communicatively registers at the beginning of each pumping chamber contrac- "tion to facilitate spilling of fuel from such chamber, the

rotor structure revolving the timing port means out of registration with the timing groove means during pumping chamber contraction to incur masking of such port by such sleeve and thus initiate fuel delivery through the distributor port, means for axially moving the sleeve relatively to the rotor structure, and means for controlling the rotative position of the sleeve during such axial move- I ment to change the relative position of the timing port means and timing -groove means circumferentially of the rotor structure axis and correspondingly change the initiating time of fuel delivery. 7

6. In a fuel metering pump; a rotor structure including a pump portion, a metering portion and a distributor portion, said pump portion having a pumping chamber and including means for alternately expanding and contracting such chamber a plurality of times attendant to each revolution of the rotor structure; means for admitting fuel to the chamber during expansion thereof; means providing a plurality of fuel delivery passages associated -with,the distributor portion; the distributor portion having a port communicative with the pumping chamber; said .port successively communicating with the delivery passages during rotation of the rotor and during respective contractions of the chamber; timing means comprising a timing port in the rotor structure metering portion'and communicating with the pump chamber, and timing port masking means associated with the rotor structure meter ing portion and adjustively movable relatively thereto for masking the timing port during periods commencing at selectively different times after commencement of respective pump chamber contractions to initiate fuel'delivery;

metering means comprising a spill port in the metering portion of the rotor structure and communicating With the pump chamber, spill port masking means associated with the metering portion. and havingspill channel means extending helically of the metering portion for registration with the spill port to facilitate. the spilling of fuel from the pump chamber through such port during such registration, the spill channel means being orientedcircurnferentially of the rotor structure to incur registration of the spill port therewith during respective masking periods of the timing port; means for adjusting the spill port masking means axially of the rotor structure to change the time after commencement of the timing port masking a pump portion having a pumping chamber; means for alternately expanding and contracting said chamber a plurality of times attendant to each revolution of said structure;'means for admitting fuel to the chamber during each expansion thereof; thejrotor structure having a distributor port communicative with the pumping chamber and revolvable attendant to rotation of said structure;

means providing a plurality of fuel delivery passages successively communicative (with the distributor port during rotation of the rotor and duringrespective contractions of the chamber; timing means comprising a timing port in 'the rotor structure and communicating with the pump "chamber, and timing port masking means associated with the rotor structure and adjustively movable relatively thereto for masking the timing port during periods com- 'mencing at selectively different times after commencement of respective pump chamber contractions to initiate, ;fuel delivery; metering means comprising a spill port in the rotor structure and revolved thereby attendant to rotor structure rotation, a spill port masking sleeve journalled on the rotor structure and having internal spill channel means extending helically of the rotor structure ;axis for registration with the spill port to facilitate the spilling of fuel from the pump chamber through such port during such registration, the spill channel means being oriented 'circumferentially of the rotor structure to incur registration of the spill port therewith during respective -masking periods of the timing port; means for adjusting the spill port masking means axially of the rotor structure ,to change the time after commencement of the timing port masking periods that registration of the spill port with the spill channel means occurs; and means operable for adjusting the spill masking means rotatively of the rotor structure for also changing the time after timing port masking period commencement that registration of the spill port with the spill channel means occurs.

8. The combination set forth in claim 3, wherein the timing channel means is in the form of a groove in the unasking means that extends helically about the rotor structure, and the means for controlling the position of the timing port masking means rotatively of the rotor istructure is adapted to constrain such masking means against rotation about the valve structure while accommodating movement of such masking means axially of the rotor structure. l

9. The combination set forth in claim 3, wherein the .timing portimasking means and the spill port masking imean'sii are respective sleeves on the rotor structure :whereon the spill port masking sleeve is axially movable and is also rotatively movable relatively to the timing port masking sleeve, said spill port masking sleeve being 'cooper'able with the spill port to vary the spill time through the spill port attendant to either axial or rotative move- ;ment, means for concurrently axially moving the sleeves, :and means for rotatively moving the spill port masking jsleeve vindependently of movement of the timing port masking sleeve to attain quantity change in fuel delivery ;-without' altering the timing of such fuel delivery.

iiefereuces Cited in the file of this, patent UNITED STATES PATENTS Bischoff June 1, 1954 

